Mechanical member for favouring the movement of means of transport

ABSTRACT

A mechanical member ( 1; 100; 200 ) for favouring the movement of means of transport which includes a support shaft ( 2; 101; 201 ), provided with a main axis (Y) and suitable to be disposed protruding from the means of transport, and sliding bodies ( 3; 108; 202 ) connected to the support shaft ( 2; 101; 201 ) through union means ( 4; 203 ), which come into contact with adjacent structures to direct the means of transport during the movement.

The present invention relates to a mechanical member for favouring the movement of means of transport, suitable especially but not exclusively for facilitating the berthing or the mooring of boats.

Well-known, the manoeuvrings with which certain means of transport, such as boats, hulls and the like are placed in the stop position, at the side of a generic support structure or other means of the same or different type, are very critical and difficult.

Considering, for example, the case of a boat which must dock at the wharf or at the pier of a harbour or which, likewise, must moor close to other boats already moored, in particularly in a predetermined space between two of them.

The difficulty is primarily determined by the combination of two reasons: the unstable nature of the surface on which the means of transport move, such as the water, and the motion direction with which these means of transport are moved in such occasions, almost always the reverse, in order to obtain a replacement on site as right and efficient as possible.

Secondly, furthermore, the laboriousness of the manoeuvrings depends on the impediments of physical nature and on the ability of the driver.

Therefore, it happens that, despite the extreme care taken on manoeuvrings by the drivers, in their movement the means of transport inevitably and accidentally hit the adjacent bodies, with the obvious problems that this implies for the structural integrity of all of them.

Furthermore, in order to limit the negative possibility just said, the drivers of the means of transport carry slowly the manoeuvrings or are forced to repeat them several times, evidently lengthening the time required for their completion, however, achieving the purpose only in isolated cases or in minimum part.

Therefore, the need to favour the moving manoeuvrings of the means of transport currently betrays, especially for the berthing to an area where there is a more or less high number of other similar means of transport, at the same time avoiding the damage both of the means of transport themselves and of any other structure or body which results to be close to them during the manoeuvrings.

To tell the truth, especially in the nautical circle, various types of equipments and components are now available on the market, mostly fenders of the inflatable type or containing spongy or rubbery material, used to eliminate or limit the harmful effects which derive from collisions between means of transport.

However, these elements, sometimes projecting from the side of the boat sometimes fixed directly to the pier or wharf, offer the opportunity to protect the means of transport from collisions only in static conditions, namely when they are moored.

Therefore, they are not fit for the use in situations where the boat or the ship is moving.

After all, the main drawback found in the known art is linked to the lack of an adequate protection against accidental collisions which the means of transport disposed in a prefixed area suffer when at least one of them is moving.

The further drawback of the laboriousness of the manoeuvrings which must be carried out to move in a safe manner, without risks of damage, the means of transport, especially for parking, mooring, docking and the like, results from this.

A last but not least drawback is due to the fact that, in many cases, the accidental collisions cause huge damage both to the means of transport which provoke them and to the other means of transport or facilities which suffer them, with the obvious disadvantages arising in terms of repair and/or replacement costs.

In the case of boats, the adverse effects of the casual collisions are magnified by the instability of the surface on which they move, which reduces their governability, and by the value of the material of the hull which suffers the collisions, often plastic reinforced by incorporated fiber glass.

The present invention aims to overcome the just cited drawbacks of the state of the art.

In particular, the main aim of the invention is to realize a mechanical member for favouring the movement of a means of transport which allows to protect the latter as any other structure from the accidental collisions generated by the means of transport while on the move, considered as the effective displacement from one site to another.

In other words, the invention intends to provide an appropriate protection to means of transport or other structures from uncontrolled collisions created by a means of transport in actual movement, for example a boat mooring or berthing at the pier or wharf of a port.

Within this aim, it is a task of the present invention to safeguard to a greater extent compared to the prior art the structural integrity of means of transport or other structures which come into contact with the means of transport in motion.

Another task of the invention is to limit with respect of the prior art the repairs and/or the replacements of structural parts damaged by accidental collisions caused by moving means of transport.

A further task of the invention is to make real a mechanical member which, in comparison to the state of the art, simplifies, making them faster and less laborious, the manoeuvrings performed by the driver to properly and effectively move a means of transport, specially in presence of other similar means or in the vicinity of any support structure.

The aforesaid aims are achieved through a mechanical member for favouring the movement of means of transport according to attached claim 1, to which it is referred for the sake of brevity.

Other features of detail of the mechanical member according to the invention are reported in the corresponding dependent claims.

Advantageously, the mechanical member of the invention is arranged on the side of a means of transport, for example on the side of a boat or the like, while the means itself is still on the move.

If the means of transport is a boat, the mechanical member of the invention is useful yet during docking, mooring or even berthing at the port, while the boat is still moving.

The mechanical member in exam thus allows to protect the means of transport to which is applied, as well as other means of transport or structures which come into contact with it, from the harmful effects resulting from the inevitable accidental collisions which occur in certain phases of its moving.

The function of the mechanical member of the invention is to mitigate to a great extent the negative effects of the collisions between the means of transport and other structures, avoiding sudden and sharp impacts between the member itself and the bodies with which it comes into contact, but rather favouring their mutual sliding.

Still advantageously, the mechanical member of which the patent-right is required simplifies with respect to the prior art the work of the driver of a means of transport during its moving in pretty critical conditions, marked by a certain massing of other means or other supporting structures in the proximity of the moving means of transport.

Indeed, in such circumstances, the invention allows the driver to perform the manoeuvrings faster than at present, without prejudicing the structural integrity of the means of transport or other bodies close to it.

Equally advantageously, through the invention the negative effects, in some cases even ruinous, arising from fortuitous collisions caused by a means of transport in motion, are strongly reduced compared to the equivalent known art.

In an advantageous manner, this helps to reduce, in comparison with the known art, the costs due to repair, replacement and, more generally, maintenance of the means of transport.

The aforesaid aims and advantages will be more evident from the description of preferred embodiments of the invention, given by way of not limiting example with respect to the attached drawings where:

FIG. 1 is a perspective view of the mechanical member according to the invention;

FIG. 2 is a side view of FIG. 1;

FIG. 3 is the view of FIG. 2 according to the cutting plane A-A;

FIG. 4 is the view of FIG. 2 according to the cutting plane B-B;

FIG. 5 is the enlarged perspective view of a first particular of FIG. 1;

FIG. 6 is a side view of FIG. 5;

FIG. 7 is the view of FIG. 6 according to the cutting plane A-A;

FIG. 8 is an enlarged side view of a second particular of FIG. 1;

FIG. 9 is a partial and simplified perspective view of FIG. 8;

FIG. 10 is an enlarged perspective view of a third particular of FIG. 1;

FIG. 11 is a side view of FIG. 10;

FIG. 12 is the view of FIG. 11 according to the cutting plane A-A;

FIG. 13 is an enlarged perspective view of a quarter particular of FIG. 1;

FIG. 14 is a side view of FIG. 13;

FIG. 15 is the view of FIG. 14 according to the cutting plane A-A;

FIG. 16 is an enlarged side view of a fifth particular of FIG. 1;

FIG. 17 is an enlarged perspective view of a sixth particular of FIG. 1;

FIG. 18 is a side view of FIG. 17;

FIG. 19 is the view of FIG. 18 according to the cutting plane A-A;

FIG. 20 is a perspective view of a seventh enlarged particular of FIG. 1;

FIG. 21 is a side view of FIG. 20;

FIG. 22 is the view of FIG. 21 according to the cutting plane A-A;

FIG. 23 is an enlarged perspective view of an eighth particular of FIG. 1;

FIG. 24 is the side view of FIG. 23;

FIG. 25 is the front view of FIG. 23;

FIG. 26 is a first different embodiment of FIG. 1;

FIG. 27 is a side view of FIG. 26;

FIG. 28 is the view of FIG. 27 according to the cutting plane A-A;

FIG. 29 is a cross section view of a second different embodiment of FIG. 1.

The mechanical member, used to favour the movement of a means of transport, preferably a boat during mooring, docking or berthing at the port, is shown in FIGS. 1 and 2, where it is generally indicated with 1.

Considering the march direction with which the boats typically reach a generic mooring or berthing site, the mechanical member 1 lends itself particularly to be installed in number of two on the sides or broadsides and in number of two abaft.

According to the invention, the mechanical member 1 includes:

-   -   a support shaft 2, clearly visible in FIG. 3, provided with a         main axis Y and suitable to be disposed protruding from the         means of transport, in this case the boat;     -   five sliding bodies 3, connected to the support shaft 2 through         union means, as a whole indicated with 4 and which come into         contact with the adjacent structures, such as boats already         moored at the pier or wharf, to direct the means of transport         during the movement in the berthing phase at the port.

As purely preferential title, the union means 4 include a pair of shaped discs 5, 6 coupled to the support shaft 2.

The sliding bodies 3 are arranged at the perimetric edge 5 a, 6 a of the shaped discs 5, 6, from which they protrude for a first stretch H, as evident from FIG. 4.

In addition, the sliding bodies 3 are equally spaced one from each other and uniformly distributed along the perimetric edge 5 a, 6 a of the shaped discs 5, 6. The main axis Y of the support shaft 2 advantageously defines for the shaped disks 5, 6 a first axis of rotation substantially vertical.

As FIG. 3 and, more in detail, FIGS. 5, 6 and 7 illustrate, the support shaft 2, made of metallic material, such as austenitic stainless alloys, is internally hollow and is provided externally with a pair of laminar flanges 7, 8 reciprocally spaced apart, coaxial to the support shaft 2.

In practice, the support shaft 2 is a tubular cylinder to which the laminar flanges 7, 8, having in this case circular shape, are externally coupled, snugly.

FIGS. 5, 6 and 7 show that each of the laminar flanges 7, 8 presents a plurality of tapered through holes 9, evenly distributed according to the vertexes of a pentagon along a first circumference C₁ substantially placed in the midpoint of the radius R of each of the laminar flanges 7, 8.

It is specified that the number of laminar flanges may also not depend on the length of the support shaft, as it will better appear later on analyzing an alternative embodiment of the invention.

The shaped discs 5, 6 are respectively arranged between the end 2 a, 2 b of the support shaft 2 and one of the laminar flanges 7, 8 to which the shaped discs 5, 6 are firmly connected through first fastening means, overall indicated with 90 in FIG. 3 and of the type in itself known, such as screws, rivets, bolts and the like.

The first fastening means 90 are inserted in the tapered through holes 9 and in female screws 10, coaxial to the tapered holes 9 and obtained in the shaped discs 5, 6.

FIGS. 8 and 9 show that the female screws 10 are evenly distributed according to the vertexes of a pentagon along a second circumference C₂ having radius equal to the radius of the first circumference C₁.

From now on and until otherwise specified, only for the sake of exposition simplicity, the description will continue with reference only to the shaped disc 5, meaning that what will be said for it also applies to the shaped disc 6.

The shaped disc 5 presents along the perimetric edge 5 a five radial indentations 11, within each of which one of the sliding bodies 3 is housed for a second stroke L.

Therefore, the number of the sliding bodies 3 is equal to the number of the radial indentations 11.

More generally, in the various forms of the mechanical member of the invention, the number of sliding bodies will always be equal to the number of radial indentations, varying in accordance with the latter.

Preferably, each of the radial indentations 11 presents a substantially U-shaped profile.

The shaped disc 5 presents a profile substantially in the shape of a star, being composed of a central block 12 and five articulated portions 13 equipped with curved outer surfaces 13 a defining an imaginary outer circumference C₄.

The articulated portions 13 project form the central block 12 according to the vertexes of a pentagon and they are spaced out one from each other by the radial indentations 11.

As a matter of fact, FIG. 9 represents only partially the shaped disc 5.

Indeed, as clearly visible in the section of FIG. 3, the shaped disc 5 is in this case formed by two laminar plates 14, 15, congruent one each other, expedient which, as it will be shortly seen, involves some significant advantages.

The laminar plates 14, 15 are reciprocally connected by using the already mentioned first fastening means, inserted both in the female screws 10 and in the further threaded through holes 16 always obtained in the shaped disc 5.

Also the threaded through holes 16 are uniformly distributed along a third circumference C₃, as it is noted in FIG. 9.

Preferably but not necessarily, the laminar plates 14, 15 are made of different materials, in particular one of a metallic material, such as aluminium, the other of polymeric material.

They may exist, however, constructive variations of the invention, not shown, in which the laminar plates are made of the same material.

According to the preferred embodiment here described of the invention, the mechanical member 1 includes five radial shock absorbers 17, visible in FIGS. 1-4, each of which housed in a peripherical seat 18 obtained in each of the outer surfaces 13 a of the articulated portions 13 of the shaped disc 5.

In FIGS. 10, 11 and 12 it is pointed out that each of the radial shock absorbers 17, real bumpers made of rubber, is composed of:

-   -   an outer cap 19 which has a convex external wall 19 a and a         concave internal wall 19 b and projects from the perimetric edge         5 a of the shaped disc 5;     -   a central separator 20, protruding from the internal wall 19 b         of the outer cap 19 and inserted in the peripherical seat 18 of         the shaped disc 5.

The peripherical seat 18 is, in fact, formed by two semi-seats one equal to the other and of the type shown in FIGS. 8 and 9.

The real peripherical seat 18 originates when, as a result of the mutual connection of the two laminar plates 14, 15, the two semi-seats overlook one each other.

Therefore, the peripherical seat 18 is derived by reciprocally combining two separate and equal parts, the laminar plates 14, 15, already obtained by moulding rather than through a machining on a monolithic piece, made of a single material, constructive solution which although most laborious is in any case included in the scope of the invention.

As far as the sliding bodies 3 are concerned, each of them includes a revolving roller 21, made of polymeric material, suitable to resist to the collisions and defining a second axis of rotation Z. The polymeric material includes any of the materials selected from the group consisting of nylon, polyoxymethylene, polyethylene and the like.

The revolving roller 21 is coupled to the shaped disc 5 through restraint means, as a whole numbered with 22 in FIG. 4.

As preferential title, the restraint means 22 include a pin 23 inserted in an axial through hole 24 made in the revolving roller 21, as can be seen in FIGS. 13-15.

The ends 23 a, 23 b of the pin 23 are housed in internal cavities 25, 26 obtained on the side walls 11 a, 11 b one opposed to the other bounding each of the radial indentations 11, as FIGS. 8 and 9 better highlight.

What has been said in relation to the formation of the peripherical seat 18 is fully valid and enforceable for the internal cavities 25, 26, each of which being composed of a first half obtained in the laminar plate 14 and a second half obtained in the laminar plate 15.

Each revolving roller 21 also presents a series of through holes 27, which develop parallely to the axis of rotation of the axial hole 24, around which they are arranged uniformly along an imaginary inner circumference C₅.

Such through holes 27 have the function of lightening the revolving roller 21 and, more in general, the mechanical member 1.

In an advantageous way, on the lateral surface 21 a the revolving roller 21 presents sliding means, overall indicated with 28, which favour the rolling friction between the revolving roller 21 and the adjacent structures with which it comes into contact. In practice, the sliding means 28 increase the rolling ability of the revolving roller 21, yet high for the system with which it is applied to the shaped disc 5 and for the material which formed it, avoiding that it scrapes against the adjacent structures, damaging them, with which it

-   -   comes into contact during the moving of the means of transport.

The presence of the sliding means 28 facilitates, for example, the release or discharge from the revolving roller 21 of strange bodies, impurities or anything else which, in certain cases, would stick to its lateral surface 21 a limiting its rotation.

In the examined case, the sliding means 28 preferably but not exclusively include two annular grooves 29 which, in other executions of the invention not mentioned in the appended drawings, can be in any number starting from one or be replaced by one or more knurled areas and similar.

In the initial FIGS. 1-3 it is also observed that the mechanical member 1 comprises a pair of axial shock absorbers 30, 31, each coupled to one end 2 a, 2 b of the support shaft 2 by second fastening means, as a whole indicated with 32.

In a preferred but not restricted way, the second fastening means 32:

-   -   a sleeve 33, also visible in FIG. 7, placed within the end 2 a,         2 b of the support shaft 2 and having a threaded central opening         34;     -   a screw 35, better shown in FIG. 16, provided with a manoeuvre         head 36, positioned within an axial housing 37 realized in each         of the axial shock absorbers 30, 31 and coaxial to the central         opening 34, and with a threaded shank 38 which engages into the         central opening 34.

For ease of exposition, it is described below the constructive form only of the axial shock absorber 30, meaning that what will be highlighted for it is valid even for the shock absorber 31.

The FIGS. 17-19 show that the axial shock absorber 30 includes a tubular insert 39 inserted into the axial housing 37 and interposed between this and the screw 35 to accommodate inside the manoeuvre head 36 of the screw 35 itself, said head 36 being suitable for example for a socket head screw.

Therefore, the axial shock absorber 30 has a composite structure in which a rigid central heart contrasts with an outer flexible and elastic zone: such a structure makes it particularly fit to absorb the accidental collisions without suffering clear pliability or deformations.

Moreover, the axial shock absorber 30 presents an flat inner wall 30 a where a series of peripheral recesses 40 is made, suitable to lighten the shock absorber 30, arranged along an imaginary circumference C₆ around a central stem 41 projecting from the inner wall 30 a.

In cross section, the axial shock absorber 30, made of rubber, presents a substantially mushroom-shaped profile while the tubular insert 39, made of brass, a substantially H-shaped profile.

Again FIGS. 1-4 illustrate that the mechanical member 1 comprises a support arm 42 for the application to a supporting structure, not shown.

The support arm 42 mainly develops along a longitudinal direction X substantially orthogonal to the main axis Y.

The support arm 42 is coupled to the support shaft 2 by means of connection, on the whole indicated with 43 in FIG. 3.

The connection means 43, shown in detail in FIGS. 20-25, include:

-   -   a shaped clamp 44, made for example in polytetrafluoroethylene         (PTFE, also known as Teflon®), locked outside the middle zone 2         c of the support shaft 2;     -   a laminar bracket 45 interposed between the support arm 42 and         the shaped clamp 44;     -   a series of screws 46 inserted into through openings 47, 48 one         coaxial to the other obtained in the shaped clamp 44 and in the         laminar bracket 45.

More in detail, the shaped clamp 44 is composed of two parallelepiped blocks 49, 50 one opposed and side by side to the other, in each of which a semi-circular cavity 51, 52 is obtained, which sets for the shaped clamp 44 a central through hole 53 in which the aforesaid middle zone 2 c of the support shaft 2 is received when the parallelepiped blocks 49, 50 are coupled one to another by means of the screws 46.

The through openings 47, 48 define longitudinal axis X′ substantially orthogonal to the main axis Y of the support shaft 2 and to the longitudinal axis of the central hole 53.

It is further observed that the laminar bracket 45 protrudes from a first end 42 a of the support arm 42, with which is monolithic, defining a plane which is perpendicularly intersected by the longitudinal direction X of the support arm 42.

In particular, the support arm 42 consists of a tubular sheet which makes it partly flexible and assimilable to a further shock absorber element which offers to the mechanical member 1 object of the invention the possibility of moving on another axis. Between the shaped clamp 44 and each of the laminar flanges 6, 7 associated to the support shaft 2 is appropriately interposed a spacer washer 54, 55, having circular shape and made for example of nylon, arranged externally coaxial to the support shaft 2. Finally, the mechanical member 1 includes a vibration-damping element 56, made of plastic material, for example rubber or polyvinylchloride (PVC).

The vibration-damping element 56 is applied to the second end 42 b of the support arm 42 and is suitable to be coupled to a generic supporting structure, already mentioned, through the use of a threaded sleeve 57 inserted in said second end 42 b.

The following figures show another embodiment of the invention where the mechanical member, now globally numbered with 100, differs from the one previously described simply for comprising a higher number of shaped discs coupled to the support arm 101, in this case four discs numbered with 102, 103, 104, 105.

You notice the presence of yet only two laminar flanges 106, 107, associated to the support shaft 101, and the particular proximity between the top pair of shaped discs 102, 103 and the lower pair of shaped discs 104, 105.

In doing so, the sliding bodies 108 of the shaped discs 102, 103 almost skim over one each other, as also the sliding bodies 108 of the shaped discs 104, 105, while the shaped discs 103 and 104 remain spaced apart one from each other by the shaped clamp 109.

The mechanical member 100 of the invention lends itself particularly for means of transport of higher dimensions, such as for example boats around 100-140 feet, while the mechanical member 1 previously described is suitable for boats of smaller dimensions, such as 30÷40 feet.

In any case, the mechanical member of the invention, yet in the versions here described, fits in use on several boats which differ in size, having lengths in the range from 30 to 140 feet.

FIG. 29 shows another embodiment of the invention in which the mechanical member, as a whole reported with 200, differs from the previous ones for including only one sliding body 202, and union means, as a whole numbered with 203, through which such sliding body 202 is connected to the support shaft 201.

It is noted that the support shaft 201 is not internally hollow, as before, but consists essentially of a linear bar.

In this regard, the union means 203 include in this case a central through hole, not shown, made axially in the sliding body 202, and the same support shaft 201 inserted in such a central hole and provided with ends 201 a, 201 b projecting from the sliding body 202. Also in this example, the axial shock absorbers 204, 205 are coupled to the ends 201 a, 201 b of the support shaft 201 through second fastening means, overall indicate with 206.

Preferably, however, the axial shock absorbers 204, 205, made of rubber, have here a profile in the shape of a hemispheric cap.

Another substantial difference of the mechanical member 200 with respect to the mechanical members 1, 100 relates to the means of connection, overall marked with 209, by which the vibration-damping element 207 is connected to the support shaft 201.

The support arm 208, still consisting of a tubular sheet and to which the vibration-damping element 207 is fixed, is no longer coupled to a shaped clamp, as in the previous cases, but to a side support 210 which is C conformed in cross section.

More specifically, the side support 210 is provided with ends 210 a, 210 b associated to the support shaft 201 and with a central part 210 c associated to the support arm 208.

In use, one or more mechanical members 1, 100, 200, the number depending on the size of the means of transport, are arranged protruding laterally from the means of transport itself while the latter is still on the move and is docking at a stop area.

In case of boats, the mechanical member 1, 100, 200 is typically arranged protruding from the sides and the stern during mooring or docking at the pier or wharf.

At that stage, the driver conveniently moves on reverse the means of transport to the stop area: in case of a boat, this means that the means of transport firstly accesses the stop area with stern. Such a manoeuvre, particularly risky and laborious in the prior art, is favoured by the mechanical member 1 which, in fact, is disposed close to the other means of transport already at stop or to any structures present in the area, without causing any damage to the parties in mutual contact.

The smooth outer surface of the rotating roller 21, its rotation around the second axis Z, the rotation of the shaped discs 5, 6 around the main axis Y of the support shaft 2, as well as the flexion ability offered by the support arm 42 realize a safety contact between the mechanical member 1 and the surrounding structures or bodies.

Therefore, the mechanical member 1 allows the means of transport where it's mounted to adjust themselves, during the movement, to the other adjacent means of transport or bodies and to occupy the space allotted to it in an easy, fast and safe manner.

Indeed, the mechanical member 1 frees itself from such bodies in an almost instantaneous and natural way, limiting to a minimum the crawling of the parts in mutual contact.

Moreover, in the collision with structures, means or other near bodies, the shape and the composition of the mechanical member 1 allow to keep integral the design and functionality thereof, unlike what will happen with equivalent systems of the known type.

At the end of the manoeuvre of access to the stop area, the mechanical member 1 is removed from the sides of the means of transport.

For example, in the nautical circle, when the boat is completely stopped, the mechanical member 1 removed from the sides and stern is replaced by the common protection systems, such as fenders.

Then, the mechanical member of the invention, for example in the alternative embodiments 1, 100, 200 described, allows the driver to perform the moving of the means of transport in absolute safety for the structural integrity of the means itself, as well as of other means of transport or similar structures which are disposed in its vicinity.

This thanks to the fact that the mechanical member according to invention helps the means of transport which brings it during the access phase to a particular area, for example for the mooring of a boat, actually positioning close to other means without compromising its own structural integrity or that of the latter during the movement.

The manoeuvring of the means of transport by the driver, especially if a boat berthing to a stop area such as the pier or the wharf of a port, appears, as a consequence, to be facilitated and requires less time to be efficiently and correctly completed.

By virtue of the above, it is understood, therefore, that the mechanical member of the invention for favouring the movement of a means of transport, especially suitable for boats, achieves the aims and realizes the advantages already mentioned.

In execution phase, modifications of the mechanical member of the invention can subsist and consist, for example, in a number and in a form of the shaped discs different from those described and illustrated above.

In addition, other versions of the invention can exist in which the mechanical member includes a number of sliding bodies different from the one indicated during the paper, variable starting from one on the basis of the project choices.

In application conditions, the main axis defined by the support shaft can be also oriented according to a direction different from those described in the previous examples, which does not affect the advantage underlying the present invention.

In addition, the mechanical member could include detection and/or signal means, such as position sensors, which in case of need signal to the driver the touch of the mechanical member with other bodies during the movement of the means of transport on which the member is mounted.

It is clear, then, that many other variations can be made to the mechanical member

-   -   in question, without for this reason going out of the novelty         principles inherent of the idea inventive, as it is clear that,         in the practical implementation of the invention, materials,         shapes and sizes of the details could be any, depending on the         needs, and could be replaced with other technically equivalent. 

1. Mechanical member (1; 100; 200) for favouring the movement of means of transport characterized in that it includes: a support shaft (2; 101; 201) provided with a main axis (Y) and suitable to be disposed protruding from said means of transport; at least one sliding body (3; 108; 202), connected to said support shaft (2; 101; 201) through union means (4; 203) and suitable to come into contact with adjacent structures to direct said means of transport during the movement.
 2. Member (1; 100) as claim 1) characterized in that said union means (4) include at least one shaped disc (5, 6; 102, 103, 104, 105) coupled to said support shaft (2; 101).
 3. Member (200) as claim 1) characterized in that said union means (203) include a central through hole, axially obtained in said sliding body (202), and said support shaft (201) inserted in said central hole and provided with ends (201 a, 201 b) projecting from said sliding body (202).
 4. Member (1; 100) as claim 2) characterized in that it comprises a plurality of sliding bodies (3; 108) placed at the perimetric edge (5 a, 6 a) of said shaped disc (5, 6; 102, 103, 104, 105) from which they protrude for at least one first stretch (H).
 5. Member (1; 100) as claim 4) characterized in that said sliding bodies (3; 108) are equally spaced one from the other and uniformly distributed along said perimetric edge (5 a, 6 a) of said shaped disc (5, 6; 102, 103, 104, 105).
 6. Member (1; 100) as any of the claims 1), 2), 4) or 5) characterized in that said main axis (Y) of said support shaft (2; 101) defines a first axis of rotation for said shaped disc (5, 6; 102, 103, 104, 105).
 7. Member (1; 100) as claim 4) characterized in that said support shaft (2; 101) is internally hollow and is externally provided with at least one laminar flange (7, 8; 106, 107) coaxial to said support shaft (2; 101).
 8. Member (1; 100) as claim 7) characterized in that said shaped disc (5, 6; 102, 103, 104, 105) presents along said perimetric edge (5 a, 6 a) one or more radial indentations (11) within each of which one of said sliding bodies (3; 108) is housed for a second stroke (L).
 9. Member (1; 100) as claim 8) characterized in that said shaped disc (5, 6; 102, 103, 104, 105) presents a profile substantially in the shape of a star, being composed of a central block (12) and a plurality of articulated portions (13) equipped with curved outer surfaces (13 a) which define an imaginary outer circumference (C₄), projecting from said central block (12) according to the vertexes of a pentagon and spaced out one from each other by said radial indentations (11).
 10. Member (1; 100) as claim 8) characterized in that each of said radial indentations (11) presents a substantially U-shaped profile.
 11. Member (1; 100) as claim 7) characterized in that said shaped disc (5, 6; 102, 103, 104, 105) is arranged between an end (2 a, 2 b) of said support shaft (2; 101) and said laminar flange (7, 8; 106, 107) to which is connected by first fastening means (90).
 12. Member (1; 100) as claim 11) characterized in that said first fastening means (90) include screws inserted in female screws (10, 16) obtained in said shaped disc (5, 6; 102, 103, 104, 105), and in tapered through holes (9) obtained in said laminar flange (7, 8; 106, 107).
 13. Member (1; 100) as claim 9) characterized in that it includes a plurality of radial shock absorbers (17), each housed in a peripherical seat (18) obtained in each of said outer surfaces (13 a) of said articulated portions (13) of said shaped disc (3, 4; 102, 103, 104, 105).
 14. Member (1; 100) as claim 13) characterized in that each of said radial shock absorbers (17), made of rubber, is composed of: an outer cap (19), which presents a convex external wall (19 a) and a concave internal wall (19 b) and projects from said perimetric edge (5 a, 6 a) of said shaped disc (5, 6; 102, 103, 104, 105); a central separator (20), protruding from said internal wall (19 b) of said outer cap (19), inserted in said peripherical seat (18) of said shaped disc (5, 6; 102, 103, 104, 105).
 15. Member (1; 100) as claim 2) characterized in that said shaped disc (5, 6; 102, 103, 104, 105) is formed by two laminar plates (14, 15), congruent one each other, reciprocally connected through said first fastening means (90).
 16. Member (1; 100) as claim 1) characterized in that said sliding body (3; 108) comprises a revolving roller (21) made of polymeric material, suitable to resist to the collisions and defining a second rotation axis (Z).
 17. Member (1; 100) as claim 16) characterized in that said polymeric material includes any of the materials selected from the group consisting of nylon, polyoxymethylene, polyethylene and the like.
 18. Member (1; 100) as claim 16) characterized in that said rotating roller (21) is coupled to said shaped disc (5, 6; 102, 103, 104, 105) through restraint means (22).
 19. Member (1; 100) as claim 18) characterized in that said restraint means (22) include a pin (23) inserted in an axial through hole (24) made in said revolving roller (21), the ends (23 a, 23b) of said pin (23) being housed in internal cavities (25, 26) obtained on the side walls (11 a, 11 b) one opposed to the other bounding each of said radial indentations (11).
 20. Member (1; 100) as claim 16) characterized in that said rotating roller (21) has a plurality of through holes (27), which develop parallelly to said rotation axis (Z) of said axial hole (24), uniformly arranged around said axial hole (24) along an imaginary inner circumference (C₅).
 21. Member (1; 100) as claim 16) characterized in that said rotating roller (21) presents on the lateral surface (21a) sliding means (28) suitable to favour the rolling friction between said revolving roller (21) and said adjacent structures with which it comes into contact.
 22. Member (1; 100) as claim 21) characterized in that said sliding means (28) include any of the constructive solutions selected among one or more annular grooves (29), one or more knurled zones and the like.
 23. Member (1; 100; 200) as claim 2) or 3) characterized in that it comprises a pair of axial shock absorbers (30, 31; 204, 205), each coupled to one end (2 a, 2 b) of said support shaft (2; 101; 201) through second fastening means (32; 206).
 24. Member (1; 100) as claim 23) characterized in that said second fastening means (32) include: a sleeve (33) placed within said end (2 a, 2 b) of said support shaft (2; 101) and having a threaded central opening (34); a screw (35) provided with a manoeuvre head (36), positioned within an axial housing (37) realized in each of said axial shock absorbers (30, 31) and coaxial to said central opening (34), and with a threaded shank (38) which engages into said central opening (34).
 25. Member (1; 100) as claim 24) characterized in that each of said axial shock absorbers (30, 31) includes a tubular insert (39), inserted into said axial housing (37), interposed between said axial housing (37) and said screw (35) to accommodate said manoeuvre head (36) of said screw (35).
 26. Member (1; 100) as claim 25) characterized in that, in cross section, each of said axial shock absorbers (30, 31), made of rubber, presents a substantially mushroom-shaped profile and said tubular insert (39), made of brass, a substantially H shaped profile.
 27. Member (200) as claim 23) characterized in that each of said axial shock absorbers (204, 205), made of rubber, presents a profile substantially in the shape of a hemispheric cap in cross section.
 28. Member (1; 100) as claim 23) characterized in that each of said axial shock absorbers (30, 31) presents a flat inner wall (30 a) where a series of peripheral recesses (40) is made, suitable to lighten each of said axial shock absorbers (30, 31) and arranged along an imaginary circumference (C₆) around a central stem (41) projecting from said inner wall (30 a).
 29. Member (1; 100; 200) as claim 7) characterized in that it includes a support arm (42; 208) for the application to a supporting structure, which develops along a longitudinal direction (X) substantially orthogonal to said main axis (Y) and is coupled to said support shaft (2; 101; 201) by means of connection (43; 209).
 30. Member (1; 100) as claim 29) characterized in that said means of connection (43) include: a shaped clamp (44; 109) locked outside the middle zone (2 c) of said support shaft (2; 101); a laminar bracket (45) interposed between said support arm (2; 101) and said shaped clamp (44; 109); at least one screw (46) inserted into through openings (47, 48), one coaxial to the other, obtained in said shaped clamp (44; 109) and in said laminar bracket (45).
 31. Member (1; 100) as claim 30) characterized in that said shaped clamp (44; 109) consists of two parallelepiped blocks (49, 50), one opposed and side by side to the other, in each of which a semi-circular cavity (51, 52) is obtained which sets for said shaped clamp (44; 109) a central through hole (53) where said middle zone (2 c) of said support shaft (2; 101) is received when said parallelepiped blocks (49, 50) are coupled one to another through said screw (46).
 32. Member (1; 100) as claim 31) characterized in that said through openings (47, 48) define a longitudinal axes (X′) substantially orthogonal to said main axis (Y) of said support shaft (2; 101) and to the longitudinal axis of said central hole (53).
 33. Member (1; 100) as claim 30) characterized in that said laminar bracket (45) protrudes from a first end (42 a) of said support arm (42), with which is monolithic, defining a plane which is perpendicularly intersected by said longitudinal direction (X) of said support arm (42).
 34. Member (1; 100; 200) as claim 29) characterized in that said support arm (42; 208) consists of a tubular sheet designed to make it partially flexible.
 35. Member (1; 100) as claim 30) characterized in that it includes a spacer washer (54) interposed between said laminar flange (6, 7; 106, 107) and said shaped clamp (44; 109), arranged externally coaxial to said support shaft (2; 101).
 36. Member (200) as claim 29) characterized in that said means of connection (209) include a C-conformed side support (210), provided with ends (210 a, 210 b) associated to said support shaft (201) and with a central part (210 c) associated to said support arm (208).
 37. Member (1; 100; 200) as claim 30) characterized in that it comprises a vibration-damping element (55; 207), made of plastic material and applied to the second end (42 b) of said support arm (42; 208), suitable to be coupled to said supporting structure.
 38. Mechanical member as substantially shown and described and for the specified purposes. 